Erector mechanism for gyroscopes



March 7, 1950- T. w. KENYQN 2,499,391

ERECTOR MECHANISM FOR GYROSCOPES Filed March 2, 1943 3 Sheets-Sheet l IN1/EN TOR. 795050,65 //FA/m/V March 7, 1950 r. w. KENYoN 2,499,391

EREcToR MECHANISM FOR GYRoscoPEs Filed March 2, 1948 3 Sheets-Sheet 2 [r] selen March 7, 1950 T. w. KENYoN 2,499,391

ERECTOR MECHANISM FOR GYROSCOPES Filed March 2, 1948 3 Sheets-Sheet 5 y ZIJ Ti 15. T1114. Kwam/(w Patented Mar. 7, 1950 2,499,391 ERECTOR MECHANISM FOR GYROSCOPES Theodore W. Kenyon, Huntington, N. Y., assgnor to Kenyon-Gyro & Electronics Corporation, Huntington, York N. Y., a corporation of New Application March 2, 194s, serial No. 12,503 1s claims. (o1. vii-'5.44)

This invention relates to gyro-verticals, and more particularly to a novel 'erecting mechanism for use in conjunction therewit An object of` the invention isto provide erecting mechanism useful with gyroscopes to erect the driven rotor axis to gyra-vertical and which is capable of accurate operation under forces up to andv including ten times the gravitational constant (10 g.)

Another object of the invention is to provide anerector mechanism by which the gyroscope is continually kept in balance at all times by the movement of erector weights thereof.

A further object of the invention is to provide simple mechanism inA conjunction With the erector mechanism to prevent actuation of operating parts of the erector mechanism during turning of a moving body or vehicle such as an airplane so that the gyro-rotor axis remains in its vertical position during execution of a turn, thereby eliminating turn error which is such an important factor in connection with high speed airplanes or missiles.

vAnother object of the invention is to embody novel'damping means in the erector system in such manner that the erector mechanism will not be affected by transient accelerations. i y

Another object-of the invention is to provide erector mechanism that can ing gy'roscopes Without material modification thereof.

To the accomplishment of the foregoing and such other objects as may hereinafter appear, the` invention comprises the novel construction and' arrangement of parts hereinafter to be described and'then sought to be defined in the appended claims, reference being had to the accompanying drawings forming a part hereof, which show merely for the purposes of illustrative disclosure, a preferred embodiment of the invention, it being expressly understood, however, that changes may be made in practice within the scope without digressingfrom the inventive idea.l

In the drawings in which similar reference characters denote corresponding parts:

Fig. 1 is a top plan view of a gyroscope equipped with an erector mechanism embodying the invention;

Fig. 2 is a side elevation thereof 'i Fig. 3 is a section takenalongline 3--3 of Fig.

2 and viewed in the direction of the arrows;

Fig. 4 is a similar vieWIv taken alongl line 4-4 of Fig. 2;

Fig. 5 is a sectional View taken along line` Ii-j-liVV of Fig. 2;

be applied to exist- .of the claims Fig. 6 is a sectional View taken along line 6-6 of Fig. 2;

Fig. 7 is an enlarged fragmentary plan View of the parts at the upper left corner of Fig. iig-illusstructural details of the turnerror elimi-V trating nating mechanism;

Fig. 8 is a fragmentary section taken along line 8-7-8 of Fig. y'I showing the parts in one position ofoperation; l

Fig. 9 is a similar sectional View showing the same parts in another position of operation;

Fig. 10 is a sectional View taken along line IIl-'-I0ofFig.1;

Fig. 1l is a sectional view taken along line II-IIofFig.5;

Fig.` 12 is a sectional View on an enlarged scale taken alongv line I2-I2 of Fig. 6;

Fig. 13 is a sectional view taken along line I3-I3of Fig. 12; and

Fig. 14 is a sectional view taken along line Ill-I4 of Fig. 12.

IReferring -to the drawings, I0 denotes in its entirety a gyro-Vertical construction.v This gyro-V vertical Hlcomprises a suitably driven gyroscope II supported for freedom of movement about mu- Y tually perpendicular horizontal axes and in substantialneutral equilibrium through the ex-` cillation about a horizontal axis which is perpendicular to that of the-bearings I3, I4 as by the axially alined oppositely located bearings I1,

I8 in said ring I2. The rotor bearing casing I5,4 if the rotor is electrically driven, includes a stator.

oi the required type and, of course, the necessary commutator on the rotor shaft, and brushes (all Y not-shown) if the gyro is a direct current type, or other necessary electrical connections (not shown) if an alternating current driven gyro is used,^or

the necessary parts for compressed* air drive ifA such a type of gyrois used.

The erector mechanism constituting the invention, denoted generally by the reference character 2l),r` is supported preferably from a plate i6- secured to the top of the rotor casing I5. This- 'erector mechanism 20vingeneral comprises a pair of shafts 2| and 22 rotatably supported at rightangles to each other Withtheir axes-lying inra common plane perpendicular to the axis 11i-Alpi therotorhshaft. Supports 23, 24, Y25 and 26-se`- cured to the plate i6 as by screws 21 are provided with bearings of appropriate type which serve to so support the shafts 2l and 22. The adjacent ends of the two shafts 2| and 22 are coupled by the meshing conical gears 28 and 29 keyed or otherwise xed to the respective shafts 2| and 22 so that these two shafts will operate in synchronism. Peripheral spiral feeding grooves or threads 3|! and 3l are provided on the surfaces of the respective shafts 2| and 22.

A spur gear 32 is keyed or otherwise secured to the remote end of one of the two shafts, for example, shaft 2|. An arcuate gear segment 33 (Fig. 11) is provided on one arm of a bell crank lever 34. This lever 36 is pivotally supported at 35 from a support 3S secured at 3'! to the plate I6. A cam follower 38 is provided on another arm of the bell crank lever 34. This cam fol. lower 38 engages an operating rod or pin 39. The

rod or pin 39 depends from an arm l5 of a bell crank lever lil (Fig. 5) which in turn is supported on a vertical shaft 42 for rotation in a plane parallel to the plane of the plate l5. The shaft 42 lies between a pair of plates 153 and All (Fig. l0). Plate d3 is supported on uprights 45 extending from the plate I6 and plate i4 issupported on uprights-llS extending from the plate i3 (Fig. 2).

A spur gear 41 (Fig. 10) secured to an eXtension of the gyro-rotor shaft (not shown) projecting upwardly of the plate i meshes with a larger diameter rst gear i8 of a gear train. The gear train includes a gear 49 coaxial with gear 48, a gear 50 meshing with gear 49, a gear 5I coaxial with gear 55, and a gear 52 meshing with the gear 5|. The opposite ends of the shaft 54 carrying the coaxial gears 48 and 9 are supported in appropriate bearings provided in the plates and 43. rIhe shaft 55 supported in bearings 56 and 57 provided in the plates 43 and M serves to support the coaxial gears 5l] and 5| on opposite sides of the plate 43. The opposite ends of the shaft 58 carrying gear 52l are supported in appropriate bearings 59 andSD (Fig. 10) provided in the plates 43 and dil so as to support the gear 52 in meshingrelationships with the gear 5|.

An eccentric cam (i2-is secured to the shaft 58 for rotation with the gear 52. The gear traincoupling gears 4l and 52 actas a speed reducing train such that gear 52 and the cam 52 driven thereby-rotate but a few revolutions per minute in contrast with thevery high rotational speed ofthe rotor driven gear 47 which is of the order of many thousands of revolutions per minute.

The bell crank lever il has an arm 33 which extends into the path of rotation of the cam 62 and is biased toward engagement therewith, as will be described, so that rotationof cam 62 causes periodic oscillation of the arm 63 and consequently bell crank lever 4| and its shaft 42. This periodic oscillation is transmitted through arm il? of bell crank lever lll to the pin or rod 39. The engagement of cam follower 38 with rod 39 imparts corresponding periodic oscillation tov the bell crank 34 and to its arcuate gear segment 33.` Since the latter meshes with-the gear 32, it

thereby causes corresponding alternate rotation in opposite directions or oscillations ofthe shaft 2| and consequent similar synchronous rotation or oscillation of shaft 22 by reason of the mesheclgears 28 Aand 29. The periodicityof alternate opposite rotational directions or oscillations of shafts- 2| and 22 corresponds to the periodicity'of the oscillations imparted to arm 63 by the cam 62.

A biasing spring (i5-acting against the bell crankA 34 (Fig. l1) biases the latter toward its uppermost position in that figure and by interaction of cam follower 38 and pin 35 biases the arm B3 against the cam 62 to eiect the described alternate opposite rotational directions of the shafts 2| and 22 during rotation of said cam 62.

Erector weights in the form of erector sleeves 5lv and 61a. are supported movably for longitudinal translation in either direction from centralized positions upon the respective shafts 2| and 22. The translatory longitudinal movements of these sleeves 61 and 67a upon the shafts 2| and 22 are controlled as will be presently describedby the described oscillatory rotations imparted toV said shafts and by additional means hereinafterto be described. Since sleeve 61 and 61a have identicall construction, the sleeve 61a only will be described in detail.

An annular centrally located groove or recess 68a isv provided in the periphery of the sleeve Sla (Figs. 2, 3, 4 and 12). symmetrical, oppositely directed; sets of wide ratchet teeth 69a and la (Figs. 34 and 4) are provided. on the surface of the sleeve Sla. on opposite sides of the centralized groove 68a. Thev outer endsl of the sleeve Glav are provided with annular lateral flanges 'ilal and 12a upstandingl from the surface of the sleeve 61a. A longitudinally extending hole 13a, is provided2 in the sleevel 61a. A spring or torsion rod Ma extends through the hole 13d and outwardlyv at the'opposite ends offsaid hole. One

gage in the spiral groove or thread 3|v of shaftA 22 (Figs. 12 and, 14'). The opposite end- 75a of theA rod 74a is bent laterally and the rod 'Illa twistedor torsioned to cause the bent end 76a to engage the peripheral surface of. the shaft 22 (Figs. 12gand 1,3) .A The, twisting or torsioning of rodV lila` causes frictional engagement of its respective ends 15d and Ilia in groove 3|' and on thesurfaces` of shaft 2,-2 so` that a friction coupling existsy between shaft 22v and sleeve 61a. Thus thelatternormally executes the same previously described rotary oscillatory movements imparted to shaftr 22y unless the sleeve is restrained frorn rotation by means tolbedescribed. In the event o f such restraint, the engagement of end 15a in spiral groove or thread 3| causes longitudinal translation of the. sleeve- @la on shaft; 22; in a direction depending upon the directionpf rotation of shaft` 22v during the period of rotational restraint of the sleeve. Similar parts numbered Gl'to 16 on the sleeve B7 that is-mounted on shaft 2|Av have identical construction.

Restraining means for acting independently on the-,sleeves'land 61a are provided. In the embodiment shown, such means comprise flexible fingers or arms 80 andta (Figs. 6 and 10). These arms 8u andila are supported respectively on pintles 8|V and Sla positioned at points 90 apart in bearings 82, 32a-provided on plate l|3v and in similar bearings provided on the plate I6. Centralizing springs 83zand 83a resembling watch hair springs havetheir opposite ends connected respectivelyy to flXedfpoints and to the respective pintles 8| and 8|a. These-springs 83 and 83a act tomaintainthe arms 8l] and Sta normally in centralized positions and crossed substantially at right anglesto eachother as-seen in Fig. 6. Pawl-like members-84 and 84a are provided on the outer-ends of arms; 813. and 38a which, in'some positions of the arms 8B' and 30a and of sleeves 61 and 61a, will lie alined with and bemovable-into theannular recesses'si and 68a of the respective sleeves 61 and 67a,

'lnbalanced weights 85, 88 and 85a, 88a are secured to the respectivearms 89 and 89a or to their pintles 8| and Bla to cause a swinging movement of the respective pintles 8| and 8|a and the arms 89 and 89a thereof whenever the gyro-rotor axis A-A deviates from vertical. The direction of such swings will depend upon the angle and direction of tilt'or deviation. Damping means 8l (Fig. 2) of desirable kind, for example, the viscous damping means described in my co-pending application, Serial No. 746,995, now Patent No. 2,464,516, is provided for-each pintle 8| and 8|'a. This damping means acts to inhibit or minimize accelerations and to average gyro-vertical deviations acting to swing the arms 89 and 89a. f y

`The` arms 89 and 89a are positioned so that theirpawls 84 and 84a normally clear the surfaces of the sleeves 91 and 61a so that they are free toswing in parallel planes parallel to the common -plane of the shafts 2| and 22 upon deviations from the vertical of the gyro axis A-A in response tov the actions of the unbalanced weights 85, 88, 85a and 86a, as limited by the damping means 81 and the restoring springs 83 and 83a. v

l.Depressing means are provided to move the pawls 84and 84a downwardly into engagement with respective surfaces of the sleeves 81 and 61a. These depressing means comprise plates 99 and 99a (Figs. 1, 2, 5 and 10) which are supported on shafts 9| and 9|a pivotally carried between respectivepairs of the supports 23, 24 and 25, 26. Biasing springs 92.9211 act normally to tend to press the outer edges 94, 94a of the plates 9| and 9|a against portions of the respective arms 89 and 89a to engage their pawls 84 and 84a. with the respective surfaces of sleeves 6l and 61a. Interengaging extensions 95, 95a of the adjacent ends of shafts 9| and 9 Ia serve to provide corresponding rotation of the shafts 9|', 9 la in opposition to the biasing springs 92 and 92aI at appropriate times as will be described.

4An extension rod 96 (Figs. 1, 5,7 and 11) securedto shaft 9| has an end portion 96a that normally overlies and engages the upper edge of the segmental gear 33 so that when the latter is in its uppermost position shown in Fig. 11 to which it is normally biased by the leaf spring 85, the shaft 9| and also shaft 9|a because of the interengaging extensions 95, 95a, are rotated in opposition to the respective biasing springs 92 and 92a. This normally maintains the edges 94 and 94a of plates 99 and 99a clear of any engagement with the arms 89 and 89a and hence the respective pawls 84 and 84a are then out of engagement with the sleeves 91 and 81a. Under such conditions the arms 89 and 89a are free to swing with their pintles 8| and Bla and the respective sleeves 61, 61a to rotate with their shafts 2| and 22 as previously described.

To eliminate turn error it is necessary to provide` means that will maintain the pawls 84 and 84a of arms 89 and 89a. out of contact with the pawls 99, 19, 69a or 19a of the sleeve 61 and 81a while the vehicle is executing a turn so that the pawls will not act upon the sleeves 61 and 81a at such times. Simple turn error eliminating means to effect this result are provided. Such means comprises an arm 98 (Figs. 1 and 5) pivotally supported at 98a for oscillation in a plane perpendicular to the axisof the gyro-rotor and, for example, from the plate 43. This arm 98 is re- Cessedor-bentat. 98h lfor clearance .relative to `the the effects of transient'v the forces caused by 75 4849 59,999.51. drirgnby the grrevrotor Shaft upright so that the latter will not interfere with necessary oscillation of the arm 98. A wide slot 98o is provided in the arm 98 through which the pin 39 passes (Fig. 11). This slot 98e is wide enough to permit necessary oscillation of the arm 98. A longitudinally extending slot 99 (Fig. 7) is provided in the free end of the arm 98. This slot 99 has oppositely tapered faces |99, |98a at the bottom face of arm 98 (Figs. 8 and 9) Vforming a widened portion for the slot 99. A pair of oppcsitely directed pre-loaded springs 19|, |92 acting on opposite side faces of the arm 98 serve to bias or center the arm 98 in a determined position. The arm 98 is displaceable in an oscillatory manner on its pivot 98a in opposition to either of the springs |91 or |92 and to either side of its determined or centered position under the action of forces created on the execution of turns by a moving body or vehicle bearing the mechanism so far described. l

An extension pin or rod portions 96a of the rod or member 98 to extend in a direction parallel with the slot 99, so as to be movable freely through the latter and an alined slot |95 in the plate 43 when the arm 98 is in its described centered or :centralized position. Normally such extension pin or rod |94 is maintained at a level above the level of the upper face of arm 98 because of the biasing action of leaf spring upon the gear segment 93 (Fig. 1l) which, in turn, acts upon the extension 95a of the rod 98 as described hereinabove. In the executions of turns, however, the arm 98 will swing to the right or left of its centralized position on its pivot 98a depending upon directions of suchv turns, to misaline the slot 99 sufficiently relative to extension |94 that a portion of the arm 98 adjacent one or the other side of the slot 99 will underlie the extension |94 and inhibit or prevent its downward movement. Such action will inhibit or prevent the biasing springs 92 and 92a from swinging their respective plates 99 and 99a and -their edges 94 and 94a into pressing engagement with portions of the arms 89 and 89a and r leave the latter free to swing and thus satisfy thev requirements of a turn error eliminating means Aas specified hereinabove.

Should the rod or element |94 happen to be in a lowered position as seen in Fig. 9 at the time the turn error arm 98 and its slot 99 are swung by a turn of the vehicle, the return stroke of the rod or element |94 will-not be impeded, forv in such return stroke it rvwill engage one or the other of the tapered faces |99, |990. and the camming action resulting from such engagement will swing the arm 98 on its pivot 98a sufficiently to permit rod |94 to pass upwardly through slot 99 to the upper side of arm 98. The latter, assuming that the turn is still occurring, will immediately be swung again to its described locking position` and preclude of rod |94 through slot 99 until the turn has been completed and the arm 98 returned to itsI centered position by the action of the springs |9| and |02.

Operation of lows:

Assuming forward motion of carrying the mechanism, the gyro-rotor driven and the sleeves 6l and 61a positioned or centralized on their shafts 2| and 22 as seen in Fig. 6

so that pawls 84 and 84a are alined with the rethe erecting mechanism is as folspective annular recesses 88 and 68a of the said,I

centralized sleeves, the gear train including gears |94 is secured to the l further downward movement the vehicle or body mounted gear il?, drives the gear 52 and with it the eccentric 52. The latter periodically oscillates the arm 53 of the bell crank d! This oscillation, in turn, is transmitted through pin 39 an'd camI 38 to bell crank 3d so that gear segment 33 is oscillated periodically about its pivotal support 3d. The gear 32 which meshes with segment 33 is thus rotated alternately in opposite directions or oscillated through about 180 in each direction. As a result, both shaft ZM and shaft 22 coupled to shaft 2i through gears 2S and 2d are similarly rotated or oscillated in synchronism. The erector weights or sleeves El and Ela on the respective shafts rotate or oscillate in similar manner as their shafts because of the slip friction coupling provided by the rod ends 'ita and 75a of sleeve @la and similar rod ends of sleeve E? so that no longitudinal or translatory movement of the sleeves on their shafts occurs.

Each time the segmental gear 33 is returned by the biasing spring 97 to its uppermost position shown in Fig. l1, the rod 96 is actuated to release position so that arms Sil and 80a are released by plates 9d and 30a and are freie to swing with their pintles 8l and 8 la. Periodic downward movement of segmental gear 33, as described, releases rod $5 and causes the biasing springs 92 andv 92a to act periodically to press the edges 96, 9la of plates 9d, @0a against the respective arms or sensitive elements 8B and Sila and to press the pawls 83 and Bla of the latter onto the respective surfaces of erector weights or sleeves E1 and 67a at Whatever positions the pawls 84 and 84a happen to be lying over said sleeves at such time. If for example, the pawl Bda happens to overlie the portion of sleeve bearing ratchet teeth 'lila caused by a swing of arm 80a to the right in Fig. 6, while the pawl 84 has remained stationary and overlies the groove 68, the downward pressure exerted by the edges 94 and 94a of the respective plates S0 and Sila will press pawl 84a against the surface of sleeve 57a over the position bearing ratchet teeth 'ma and simply press pawl 84 into groove 68. In consequence, sleeve 6l will not move along shaft 2|. Pawl 84a, however, will ride over teeth 'ma in one direction of rotation of shaft 22 and sleeve Sla but will engage one of the ratchet teeth lila in the opposite rotation of shaft 22, and at such time lock the sleeve against rotation. This will cause a longitudinal translation or movement of the sleeve @la on shaft 22 in an erecting direction because of the feeding action cf spiral groove 3l on the rod end 15a (Fig. l2). The flanges li, l2, 'ila and- 72a on the sleeves prevent the pawls from riding 0H the outer ends of the respective sleeves 67 and 61a. Similar longitudinal translations in appropriate directions of either of the sleeves 61 or Gla will occur upon any right or left shifts or movements of the pawls 8d or alla caused by corresponding shifts or swings of their carrying arms or sensitive elements 88 or 30a. These shifts or swing movements of arms 88 or Sila are effected by the respective unbalanced weights 85, 86, 85a, 86a periodically while arms 8G or 80a are free to swing, as a result of deviations from the vertical of the gyro-rotor axis A-A. The extentA of swing is averaged by the damping means 87 on the pintles 8l and Bla in accord with the extent of deviation from the vertical of thesaid rotor axis A-A The damping means el also minimize or inhibit the effects of transient accelerations on the position of such' arms Sil and 30a.

The longitudinal displacements of the sleeves 61' and 61a acting as erector weightsY on' their respective shafts from centralized or balanced positions which are effected as just described are always in directions to cause a counter precessional movement or erecting action on the gyro to restore its rotor axis to substantially vertical or initial erect position. The movement of each erectorvweight or sleeve 87 or 61a continues in such an erecting direction until sufficient precessional action has been effected by its unbalanced position thereon to begin precessional restoring movements of the gyro-rotor axis A-A. When this occurs the unbalanced weights 85, 86, a, 86a move the arms 8G and 80a in opposite directions from that to which they have been movedv to cause periodic interaction of their pawls 84 and 84a with the oppositely directed ratchet teeth 5S, lll, 69a and 'lila on the respective` sleeves 61 and 61a and thereby effect return longitudinal movement of the said sleeves 61 and 51a toward their initial centered or centralized positions which positions are achieved substantially shortly after the gyro-rotor axis A-A has been returned to its normal vertical position'. Briefly the periodic controlling interaction of the pawls 8d and 84a with the opposite-ly directed ratchet teeth 69, l0, 69a and 'Illa of the respective shaft borne rotatable erector weights or sleeves 631 and 67a causes longitudinal translation of these weights from centralized or balanced positions on the respective shafts 2l and `22 in necessary directions to cause precessional erecting action created by unbalanced or off centralized positions of such erector weights, and a restoration of said weights or sleeves toward initial centralized or balanced positions substantially when erecting action has been completed and the gyro-rotor axis A-A has beenA restored to vertical.

During execution of turns, the turn error arm S3 and its associated components act as described hereinabove to preclude pressing engagement and action of the pawls 84 and 34a on the ratchet teethv 89, lo, 63a and lila of the respective erector weights or sleeves 61 and 61a. The arm 98 bef comes inactive immediately upon completion of the turn under positioning control of the preloaded springs lili and |02 as described and the erecting mechanism is then again free to act.

The speed of rotation of the eccentric 62 is made sucient through' the gear train connecting gears 41 and 52 to insure suiciently frequent oscillations of gear segment 33 and periodic, alternate engagement and clearance of the pawls 84j and 84a with the ratchet teeth 69, lil, 69a and ma, as the case may be, to provide the described translato'ry movements of the erector weights or sleeves 6l! and @la on their shafts 2i and 22 necessary for substantially continual gyro-vertical erecting `control of the axis A-A of the gyrorotor. Since the erecting weights El and fila require positive interaction therewith of the pawls 84 and 34a for required translations on their shafts 2| and 22, transient accelerations have no material effects. Moreover, other inaccuracies are prevented which are likely to occur when the vehicle carrying the described erecting mecha nism travels at high speeds and provides forces up to ten times the gravitational constant (l0 g).

The structure disclosed is comparatively simple mechanically and entirely effective for the inu tended purposes. It provides an effective erector mechanism whereby the gyroscope is continually operated to balance it to gyro-vvertical at all times and wherein turn error is eliminated.

While a specic' embodiment of thev invention has been disclosed, variations in detail within the 'scope of the claims are possible and are contemplated. There is no intention therefore of limitation to the exact details shown and described.

What is claimed is:

1. Erector mechanism for erecting the axis of the driven rotor `of a gyroscope to gyro-vertical comprising a pair of erector weights positioned at centralized positions for movements at right angles relative to each other, means driven by said rotor for moving said weights, and. means responsive to deviation of the gyroscope axis from gyro-vertical positions to effect interaction between said weight moving means and said weights to cause the latter to be moved at right angles relative to each other and independently from their centralized positions to gyra-erecting positions. 'Y

2. Erector mechanism for maintaining gyrovertical of the axis of a driven gyroscope rotor comprising a pair of shafts mounted-at right angles to each other in a plane perpendicular to the rotor axis, driving means for oscillating the two shafts, erector weights, one mounted on each of said shafts, and shifting means for causing movement of each weight independently along its oscillating shaft in an erecting direction in response to deviations of the rotor axis from gyro-vertical position;

3. Erector mechanism for maintaining gyrovertical of the axis of a driven gyroscope rotor comprising a pair of shafts mounted at right angles to each other in a'plane perpendicular' to i the rotor axis, driving means 'for oscillating the two shafts simultaneously, a gear train coupling said driven rotor to said driving means, erector weights., one mounted on each of said shafts, and shifting means for causing movement `o`f 'each weight independently along its' oscillating shaft in an erecting direction in response to deviations of the rotor axis from gyro-vertical position.

4. Erector mechanism for maintaining gyrovertical of the axis of a driven gyroscope rotor comprising a pair of shafts mounted at right angles to each other in a plane perpendicular to the rotor axis, driving means for oscillating the two shafts, erector weights, one mounted on each of said shafts, each shaft having a spiral groove, frictional means coupling each weight with the spiral groove on its supporting shaft and also to its shaft to cause simultaneous similar oscillation of each weight with the oscillation of its supporting shaft, oppositely directed ratchet teeth on each weight and separate pawl means each having positional responses in accord with deviations of the rotor axis from gyro-vertical position for engagement with the said ratchet teeth on a different one of said weights for preventing rotary movement of such weights in required direction and thereby causing longitudinal translations of the weights along their shafts by the actions of the spiral grooves on the respective frictional means coupled therewith.

5. In a device as per claim 4, arms to ea-ch of which one of said pawl means is attached and means connected with said arms to cause the latter to swing independently in response to deviations of said rotor axis from gyro-vertical positions.

6. In a device as per claim 5, centralizing springs for returning said arms to centralized positions, and damping means for averaging swing of said arms.

7. In a device as per claim 4, spring-biased 10 means for periodically pressing said pawl means into engagement with the ratchet teeth on respective of said weights during rotary oscillations of said shafts.

8. In a device as per claim 7, turn error eliminating means for inhibiting action of said springbiased means during the execution of turns by a moving body carrying said erector mechanism.

9. In a device as per claim 7, a projection on said spring-biased means, and a normally centralized arm engageable with said projection in non-centralized positions effected during execution of turns by a moving body carrying said erector mechanism to inhibit said pressing action of said spring-biased means during such turn executions.

10. In a device as per claim 2 in which said shifting means includes a threaded portion, a member secured to each weight for engagement frictionally with such a threaded portion on each shaft, ratchet teeth on each weight, pawlcarrying arms Whose pawls are engageable one with the ratchet teeth of each one of said weights, and periodically operated means for pressing the pawls into such engagement.

11. In a device as per claim 10, turn error eliminating means for inhibiting the action of the periodically operated means during the executions of turns by a moving body carying said erector mechanism.

12. In a device as per claim 1, turn error eliminating means rfor said mechanism.

13.4 Erector mechanism for erecting the axis of n the driven rotor of a gyrosccpe to gyra-vertical comprising a pair of sleeve-like erector weights each having symmetrically disposed oppositely directed sets of ratchet teeth, a pair of rotatable shafts positioned at right angles to each other in acommon plane perpendicular to the rotor .axis onVv each of which one of said weights is mounted for longitudinal movement relative to la centralized position, gear train means for periodically oscillating the two shafts synchronously on their respective axes, each shaft having a spiral groove, frictional means connecting each sleeve to the spiral groove of the shaft on which it is mounted to effect longitudinal movement of the sleeves relative to their shafts whenever the sleeves are held against rotation with their shafts, pawl-bearing swingable arms swingable in planes parallel to the said common plane, whose pawls are each engageable respectively with the sets of ratchet teeth on a different sleeve, and springbiased means operable to press the pawls into engagement with underlying ratchet teeth of the sleeves periodically during oscillating rotation of the shafts and thereby to effect said longitudinal movement of said sleeves on their shafts.

14. In a device as per claim 13, turn error eliminating means comprising an arm engageable with a portion of said spring-biased means during executions of turns by a moving body carrying said mechanism to then preclude pressing operation of said spring-biased means upon said pawls.

15. Erector mechanism for maintaining gyro vertical of the axis of a driven gyroscope rotor Kcomprising a pair of shafts mounted at right angles to each other in a plane perpendicular to the rotor axis, each shaft having a threaded portion, driving means for oscillating the two shafts, erector weights, one mounted for longitudinal translation on each of said shafts, a member secured to each weight for engagement frictionally with the threaded portion of the shaft upon 11 which the weight is mounted so that normally each Weight oscillates with the shaft on which it is mounted, ratchet teeth on each Weight, pawlcarrying swingable arms Whose paWls are engageable one with the ratchet teeth of each one of said weights, and periodically operable meansv for pressing the pawls into such engagement to then restrain oscillation of the Weights with the shafts on which they are mounted, thereby causing the irictional means ci `the weights while the weights are restrained to interact With the threaded portions of the shafts to eiect longitudinal translation of the weights on their shafts.

16. Erector mechanism for erecting the axis of the driven rotor or" a gyroscope to gyro vertical comprising a pair of erector sleeves each having symmetrically disposed oppositely-directed sets of ratchet teeth on its surface separated by a centralized recess, a pair of rotatable shafts positioned at right angles to each other in a common plane perpendicular te the rotor axis on`each of which one oi said weights is mounted for longitudinal movement relative to a! centralized position, gear train means driven by the roto-r for periodically oscillating the tWo shafts on their respective axes, each shaft'having a spiral groove, frictional means connecting each sleeve to the spiral groove of the shaft on Which it is mounted to effect longitudinal movement of the sleeves relative to their shafts Whenever said sleeves are held against rotation with their shafts, pawlbearing swingable arms swingable in planes parallel to said common plane whose pawls overlie and are engageable respectively with the sets of ratchet teeth on a different sleeve on opposite sides of the centralized recess of the sleeve, spring-biased means operable periodically during oscillating rotation of the shafts to press the pawls into engagement with those ratchet teeth of the sleeves underlying the pawls Whenever the spring-biased means are operated and thereby to effect said 'longitudinal 'movement of Vsaid sleeves on their shafts, and means to control the periodicity of operation of said springbiased means( 17. Erector mechanism for erecting the axis of the driven rotor of a gyroscope to gyro Vertical comprising a pair of erector sleeves positioned at centralized positions for movements at right angles relative to each other, oppositely directed sets of ratchet teeth on each sleeve, means driven by said rotor for moving said sleeves and means responsive to deviation of the gyrosccpe aXis from gyro vertical positions and including pawlcarrying swingable arms Whose pawls are engageable one with each of the sets of ratchet teeth of a different sleeve to elect interaction between said sleeve moving means and said sleeves to cause the latter to be moved at right angles to each other and independently from their centralized positions to gyro-erecting positions,

18. A device as per claim 17 in which the oppositely directed sets of ratchet teeth on each sleeve are separated by a centralized recess and in which the outer ends of each of the sleeves have laterally extending annular anges.

THEODQRE W. KENYON.

REFERENCES CITED The following references are of record in the nle of this patent:

UNITED STATES PATENTS 

